JPS5845617B2 - transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a transmission suitable for use in combination with a fluid coupling for a vehicle, particularly for an automobile.

It is desirable for a transmission device for a large vehicle such as a truck or bus to have at least four or more gear stages.

For this reason, a single pinion planetary gear set is used.
It is conceivable to realize four or more gear stages by combining a set, four or more sets, and appropriately connecting each element therein.

Although a large number of combinations of transmissions are possible, it is desirable that the following conditions be satisfied.

(1) The output shaft must be connected to the same element for each gear stage.

(2) The number of teeth of each gear in each planetary gear set must satisfy the meshing conditions, and the sun gear and planetary gear with the minimum diameter must also have the required number of teeth or more.

(3) The connection relationship between each element of each planetary gear set can be easily achieved with a length as short as possible.

(4) When changing gears while driving, the frictional engagement means are switched to change gears, but this switching can be done by only one switch in order to reduce the switching shock.

Taking these conditions into account, the present invention basically uses three sets of single-pinion simple planetary gear sets, basically uses three sets as clutch devices, and basically two sets as brake devices, and each planetary gear It is an object of the present invention to provide a transmission having at least four forward gears and one reverse gear by appropriately coupling movable members of a set and appropriately disengaging a clutch device and a brake device.

Embodiments of the present invention will be described below with reference to the accompanying drawings.

The first embodiment of the device of the present invention will be explained with reference to FIG. 1. Between the input shaft and the output shaft, there are a single pinion type first planetary gear set X1, a second planetary gear set X2,
A third planetary gear set X3 is present.

The first planetary gear set X1 includes a first sun gear S
1, a first ring gear RG1 that meshes with the first sun gear, and a first carrier C1 that pivotally supports the first planetary gear P1.
and has.

The second planetary gear set X2 is a second sun gear S.
2, a second planetary gear P2 that meshes with the second sun gear, a second ring gear RG2 that meshes with the second planetary gear, and a second carrier C that pivotally supports the second planetary gear P2.
It has 2.

Similarly, the third planetary gear set X3 includes a third sun gear S3, a third planetary gear P3 that meshes with the third sun gear, and a third ring gear R that meshes with the third planetary gear.
G3 and a third carrier C3 that pivotally supports the third planetary gear P3.

The input shaft and the first sun gear S1 are drivingly connected.

The first carrier C1 and the second ring gear RG2
is drivingly connected.

The second sun gear S2 and the third sun gear S3 are drivingly connected.

A first clutch CL1 is provided between the input shaft, the second carrier C2, and the third ring gear RG3, and is configured to integrally connect or disconnect the input shaft, the second carrier C2, and the third ring gear RG3. is installed.

A second clutch is provided between the input shaft, the first carrier C1, and the second ring gear RG2 to integrally connect or disconnect the input shaft, the first carrier C1, and the second ring gear RG2. CL2 is provided.

Between the first ring gear RG1 and the second carrier C2, the first ring gear RG1 and the second gear C2 are connected.
A third clutch CL3 that integrally connects and disconnects the two is provided.

CL4 is a fourth clutch connected in parallel with the third clutch CL3, and only when the relative rotation between the first ring gear RG1 and the second carrier 02 is in one direction, the first ring gear RG1 and the second carrier C2 are connected. It is a one-way clutch that engages or releases the

A first brake B1 is provided between the second carrier C2, the third ring gear RG3, and the case, so that when the brake is activated, the second carrier C2 and the third ring gear RG3 can be fixed. It has become.

Said 2nd and 3rd sun gear S2. A second brake B2 is provided between B3 and the case, and when the brake is activated, it can lock the second and third sun gears S2°B3.

and each planetary gear set Xi, X2.

In X3, the following formula (the same applies to all embodiments described below).

) holds true. However, NRGl, NHO2, NHO3...first, second
, number of rotations of the third ring gear NC1, NC2, NC3...first, second, third
Carrier rotation speed NS1, NS2, NS3...1st, 2nd, 3rd
Sun gear rotation speed ■1, ■2, ■3... The radius ratio of each ring gear and each sun gear.

Here, to give an example of specific numerical values of each gear stage of the transmission according to the present invention, I,=0.484.12=0.453.
13=0.438 (the same applies to all the examples described below).

), and the operation of the clutches CL1, CL2, CL3, CL4 and brakes B1, B2 at each gear of the transmission of the present invention and the relationship of the reduction ratio of each gear are summarized as shown in Table 1.

However, Fn (n=1.2.3...) indicates a forward gear stage; for example, Fl indicates first forward gear, F2 indicates second forward gear, and R indicates reverse gear.

Next, a second embodiment of the device of the present invention will be explained with reference to FIG.
In the embodiment shown in FIG. 1, a single pinion type fourth planetary gear set X4 is interposed between the third planetary gear set X3 and the output shaft, and the connection relationship with each element is as follows. It is.

The fourth planetary gear set X4 includes a fourth sun gear, a fourth planetary gear that meshes with the fourth sun gear, a fourth ring gear RG4 that meshes with the fourth planetary gear, and a fourth carrier C4 that pivotally supports the fourth planetary gear. have

The fourth ring gear RG4 is drivingly connected to the third sun gear S3, and when the second brake B2 is operated,
Similarly to the third sun gear S3, the fourth ring gear RG4 is fixed.

A third brake B3 is provided between the fourth carrier C4 and the case, and when the third brake B3 is operated, the fourth
It is designed so that the carrier C4 can be secured.

The fourth sun gear S4 is dynamically and integrally connected to the output shaft.

The following equation holds true in the fourth planetary gear set X4.

However, NHO4...-4th ring gear rotation speed NC4.
...Rotation speed of 4th carrier NS4 ...Rotation speed of 4th sun gear ■4...
... The radius ratio of the 4th ring gear and the 4th sun gear.

Here, to give an example of specific numerical values for each gear stage of the transmission device according to the present invention, 14=0.5, and each clutch CLI, CL2,
CL3, CL4 and each brake Bl, B2. Table 2 summarizes the relationship between the operation of B3 and the reduction ratio of each gear stage.

Next, a third embodiment of the device of the present invention will be explained with reference to FIG.
This embodiment is similar to the second embodiment shown in FIG. 2, in which a single pinion fourth planetary gear set X4 is provided between the third planetary gear set X3 and the output shaft in the first embodiment shown in FIG. It is a configuration formed by intervening elements, and the connection relationship with each element is as follows.

The fourth sun gear S4 is drivingly connected to the third sun gear S3, and when the second brake B2 is operated, the fourth sun gear S4 is locked like the third sun gear S3.

A third brake B3 is provided between the fourth carrier C4 and the case, and is configured to clamp the fourth carrier C4 when the brake is activated.

The fourth ring gear RG4 is dynamically and integrally connected to the output shaft.

Here, to give an example of the numerical value of the specific gear position of the transmission according to the present invention, it is 14=0.548, and the operation of each clutch and each brake at each gear position of the transmission apparatus of the present invention and the operation of each gear position of each gear position are as follows. Table 3 summarizes the relationship between reduction ratios.

As is clear from the above explanation, according to the present invention, there are basically three
If the initial purpose can be achieved distantly by using two planetary gear sets, and if (1) the frictional engagement means is interposed between both planetary gear sets, the connection relationship is maintained. It can be placed at any position around the target planetary gear set, and has a high degree of freedom in placement.

(2) Since the reverse brake, which requires a large torque transmission capacity, is not used when moving forward, automatic gear shift shock control is advantageous.

(3) When a friction engagement means and a one-way clutch are used together, torque transmission can be shared between both clutches, the torque transmission capacity of the friction plates can be reduced, and the number of friction plates can be reduced. It becomes possible.

At least 4 advances which have advantages such as
It is possible to obtain a gear stage of 1 reverse gear and 1 reverse gear, which has great industrial effects.

[BRIEF DESCRIPTION OF THE DRAWINGS] FIG. 1 is a schematic central longitudinal cross-sectional view diagrammatically showing a first embodiment of the transmission of the present invention, and FIG. 2 is a diagrammatic diagram of a second embodiment of the transmission of the present invention. FIG. 3 is a schematic central vertical cross-sectional view diagrammatically showing a third embodiment of the transmission of the present invention. XI: 1st planetary gear set, X2: 2nd planetary gear set, X3: 3rd planetary gear set),
SL: 1st sun gear, B2: 2nd sun gear, B3: 3rd
Sun gear, Pl: 1st planetary gear, P2: 2nd planetary gear, P3: 3rd planetary gear, RGl: 1st planetary gear.
Ring gear, RG2: second ring gear, RG3: third ring gear, C1: first carrier, C2: second carrier,
C3: Third carrier, CLl: First clutch, CL2:
2nd clutch, CL3: 3rd clutch, CL4: 4th clutch, B1: 1st brake, B2: 2nd brake.

Claims (1)

[Scope of Claims] 1. Several sets of planetary gears each consisting of a human power shaft, an output shaft, a carrier that pivotally supports a sun gear, a ring gear, and a planetary gear that meshes meshing motion between the two gears, and a case that is a fixed member. the sun gear of the first planetary gear set is drivingly connected to the input shaft, the carrier of the first planetary gear set and the ring gear of the second planetary gear set are drivingly connected, and the carrier of the second planetary gear set and the third planetary gear The ring gear of the third planetary gear set is drivingly connected, the sun gears of the second and third planetary gear sets are drivingly connected, the carrier of the third planetary gear set is drivingly connected to the output shaft, and the carrier of the third planetary gear set is drivingly connected to the output shaft. one clutch that connects or releases the carrier of the third planetary gear set and the ring gear of the third planetary gear set with respect to the input shaft;
Another clutch connects or releases the carrier of the first planetary gear set and the ring gear of the second planetary gear set connected to the input shaft, and the carrier of the second planetary gear set and the ring gear of the third planetary gear set are connected to each other. a first brake capable of fixing the carrier of the second planetary gear set and the ring gear of the third planetary gear set to the case; , and a second brake capable of fixing the sun gears of the second and third planetary gear sets connected to the case. 2 A human power shaft, an output shaft, several planetary gear sets each consisting of a sun gear, a ring gear, and a carrier that pivotally supports a planetary gear that meshes meshing motion between the two gears, a case that is a fixed member, and a first planetary gear set. The sun gear of the first planetary gear set is drivingly connected to the input shaft, the carrier of the first planetary gear set and the ring gear of the second planetary gear set are drivingly connected, and the carrier of the second planetary gear set and the ring gear of the third planetary gear set are driven. The sun gears of the second and third planetary gear sets are drivingly connected, the carrier of the third planetary gear set is drivingly connected to the output shaft, and the carrier of the second planetary gear set and the third planetary gear A clutch that connects or releases a set of ring gears to an input shaft,
Another clutch connects or releases the carrier of the first planetary gear set and the ring gear of the second planetary gear set connected to the input shaft, and the carrier of the second planetary gear set and the ring gear of the third planetary gear set are connected to each other. a first brake capable of fixing the carrier of the second planetary gear set and the ring gear of the third planetary gear set to the case; , and a second brake capable of fixing the connected sun gears of the second and third planetary gear sets to the case, and any two of the sun gear, ring gear, and carrier of the fourth planetary gear set. One is drivingly connected to the output shaft, and the other is drivingly connected to the sun gear of the second and third planetary gear sets, and the sun gear, ring gear, and carrier of the fourth planetary gear set. A transmission device comprising a third brake capable of fixing the remaining members of the casing to the case.